US10876621B2 - Power transmission device - Google Patents

Power transmission device Download PDF

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Publication number
US10876621B2
US10876621B2 US15/921,668 US201815921668A US10876621B2 US 10876621 B2 US10876621 B2 US 10876621B2 US 201815921668 A US201815921668 A US 201815921668A US 10876621 B2 US10876621 B2 US 10876621B2
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Prior art keywords
planetary gear
rotary shaft
lubricant
gear mechanism
gear
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US15/921,668
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US20180274655A1 (en
Inventor
Junichi Yamaguchi
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Assigned to HONDA MOTOR CO.,LTD. reassignment HONDA MOTOR CO.,LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YAMAGUCHI, JUNICHI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0424—Lubricant guiding means in the wall of or integrated with the casing, e.g. grooves, channels, holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0426—Means for guiding lubricant into an axial channel of a shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0484—Gearings with gears having orbital motion with variable gear ratio or for reversing rotary motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2066—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using one freewheel mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
    • F16H2200/2082—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches one freewheel mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another

Definitions

  • the disclosure relates to a power transmission device, and more particularly, to a structure for lubricating a bearing which is disposed on an outer circumferential surface side of a rotary shaft for transmission of power.
  • a lubricant is supplied to a bearing which is disposed on an outer circumferential surface of a rotary shaft.
  • the supply of a lubricant is performed via a lubricant passage which is formed inside the rotary shaft.
  • the lubricant passage extends in an axial direction inside the rotary shaft and a lubricant is supplied from one end of the lubricant passage.
  • a discharge channel that is opened to the outer circumferential surface is formed in the rotary shaft, and the lubricant supplied to the lubricant passage flows to the bearing via the discharge channel with rotation of the rotary shaft.
  • a lubricant supplied to the lubricant passage is discharged to the outside of the rotary shaft when the lubricant reaches the other end of the lubricant passage due to an influence of a centrifugal force of the rotating rotary shaft. Accordingly, for example, there is concern that a bearing rotatably supporting the rotary shaft at the other end of the rotary shaft will not be sufficiently lubricated.
  • a lubricant supply structure in which a lubricant is guided to a desired position in the lubricant passage via a tube member by providing the tube member extending over the whole length in the lubricant passage of the rotary shaft and forming a communication hole communicating with the lubricant passage on an outer circumferential surface of the tube member is known (for example, see Patent Document 1).
  • the tube member is fixed to a housing that rotatably supports the rotary shaft. Since a lubricant in the tube member is not affected by a centrifugal force based on rotation of the rotary shaft, a sufficient amount of lubricant is supplied from one end of the tube member to the other end. Accordingly, a sufficient amount of lubricant can be supplied to the bearing that rotatably supports the rotary shaft at the other end of the rotary shaft.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2000-240772
  • An exemplary embodiment of the disclosure provides a power transmission device including: a rotary shaft (for example, an idling shaft 23 in an embodiment, which is the same in the following description) that is provided in a housing (for example, a transmission case 10 in the embodiment, which is the same in the following description); a lubricant passage (for example, a lubricant passage 231 in the embodiment, which is the same in the following description) that is formed in the rotary shaft and is opened at an end of the rotary shaft; a bearing (for example, a first bearing BRG 1 in the embodiment, which is the same in the following description) that is provided between an outer circumference of an end of the rotary shaft and the housing and rotatably supports the rotary shaft; and a discharge channel (for example, a discharge space 233 in the embodiment, which is the same in the following description) that discharges a lubricant in the lubricant passage in a radial direction from the opening at the end of the rotary shaft to supply the lubricant to the
  • the discharge channel may include a second annular protruding portion (for example, a second annular protruding portion 233 b in the embodiment, which is the same in the following description) that is formed on the inner surface of the housing facing the axial direction of the rotary shaft and protrudes to an inner circumferential edge of the opening of the rotary shaft.
  • a second annular protruding portion for example, a second annular protruding portion 233 b in the embodiment, which is the same in the following description
  • the opening of the rotary shaft may include an inclined surface (for example, an inclined guide surface 231 b in the embodiment, which is the same in the following description) that expands gradually from the inside of the lubricant passage to the outside of the opening.
  • an inclined surface for example, an inclined guide surface 231 b in the embodiment, which is the same in the following description
  • FIG. 1 is a diagram schematically illustrating a vehicle in which a power transmission device according to an embodiment of the disclosure is mounted;
  • FIG. 2 is a skeleton diagram illustrating a gear shift mechanism which is the power transmission device according to the embodiment
  • FIG. 3 is a nomogram illustrating the gear shift mechanism which is the power transmission device according to the embodiment
  • FIG. 4 is a diagram illustrating engagement states of engagement mechanisms in gear shift stages in the embodiment
  • FIG. 5 is a sectional view illustrating a fixed state of a two-way clutch which is employed in the embodiment
  • FIG. 6 is a sectional view illustrating a reverse rotation prohibited state of the two-way clutch which is employed in the embodiment
  • FIG. 7 is a perspective view illustrating the fixed state of the two-way clutch which is employed in the embodiment.
  • FIG. 8 is a perspective view illustrating the reverse rotation prohibited state of the two-way clutch which is employed in the embodiment.
  • FIG. 9 is a sectional view illustrating principal parts in the embodiment.
  • FIG. 10 is an enlarged view illustrating a part of FIG. 9 .
  • the bearing supporting the rotary shaft is provided on the outer circumference of an end position of the rotary shaft and has a smaller protruding length outward from the end face in the axial direction of the rotary shaft. Since a lubricant discharged outward from an edge of the lubricant passage due to the centrifugal force resulting from rotation of the rotary shaft strongly flows in a direction perpendicular to an axis of the rotary shaft, the lubricant flows outward past the bearing with almost no contact with the bearing. Accordingly, even when a sufficient amount of lubricant is supplied from the edge of the lubricant passage, there is concern that lubrication of the bearing will not be satisfactory.
  • An aspect of the disclosure is to provide a power transmission device that can satisfactorily supply a lubricant from a lubricant passage which is formed in a rotary shaft.
  • the first annular protruding portion by providing the first annular protruding portion on the inner surface of the housing, a lubricant flowing from the end of the lubricant passage into the discharge channel is guided over the first annular protruding portion. Since the first annular protruding portion protrudes between the rotary shaft and the bearing, the lubricant guided to the first annular protruding portion flows to the bearing. Accordingly, it is possible to satisfactorily supply the lubricant past the lubricant passage of the rotary shaft to the bearing.
  • the lubricant flowing along the inner surface of the lubricant passage and colliding linearly with the inner surface of the housing is smoothly changed in direction to a radial direction by a second annular protruding portion. Accordingly, the lubricant flowing along the inner surface of the lubricant passage can be smoothly curved in the radial direction to flow to a discharge space.
  • the lubricant flows along the inclined surface to form a flow in the radial direction due to the centrifugal force of the rotary shaft. Accordingly, it is possible to cause the lubricant flowing along the inner surface of the lubricant passage to flow to the discharge space.
  • a vehicle V includes a power transmission device PT according to the embodiment and an engine E (an internal combustion engine as a drive source, where an electric motor may be used instead of the engine E) in which a crank shaft 1 is horizontally arranged to be parallel to a right-left direction of a vehicle body).
  • an engine E an internal combustion engine as a drive source, where an electric motor may be used instead of the engine E
  • a crank shaft 1 is horizontally arranged to be parallel to a right-left direction of a vehicle body
  • a driving force output from the engine E is transmitted to the power transmission device PT.
  • the power transmission device PT adjusts the driving force of the engine E to correspond to a selected gear shift ratio and transmits the adjusted driving force to front-right and front-left wheels WFL and WFR.
  • the power transmission device PT includes a torque converter 2 that is connected to the crank shaft 1 , an automatic transmission 3 that is connected to the torque converter 2 , and a front differential gear 4 that is connected to the automatic transmission 3 .
  • the power transmission device PT having this configuration is controlled by a gear shift controller ECU.
  • the front differential gear 4 is connected to the front-right and front-left wheels WFL and WFR via a front-left axle 7 L and a front-right axle 7 R.
  • FIG. 2 is a skeleton diagram of the automatic transmission 3 .
  • the automatic transmission 3 includes an input shaft 11 serving as an input member which is rotatably supported in a transmission case 10 serving as a housing and an output member 13 including an output gear disposed to be concentric with the input shaft 11 .
  • a driving force from the engine E is transmitted to the input shaft 11 via the torque converter 2 including a lockup clutch and a damper.
  • Rotation of the output member 13 is transmitted to right and left driving wheels (front wheels WFR and WFL) of the vehicle via an idling gear 21 that engages with the output member 13 , an idling shaft 23 corresponding to a rotary shaft in the embodiment of the disclosure and axially supporting the idling gear 21 , a final drive gear 25 that is axially supported by the idling shaft 23 , and a front differential gear 4 including a final driven gear 27 that engages with the final drive gear 25 .
  • a single-disc type or multi-disc type starting clutch configured to frictionally engage may be provided instead of the torque converter 2 .
  • a propeller shaft may be provided instead of the front differential gear 4 for application to a rear-wheel-drive vehicle.
  • a propeller shaft may be connected to the front differential gear 4 via a transfer for application to a four-wheel-drive vehicle.
  • the third planetary gear mechanism PG 3 is configured as a so-called single pinion type planetary gear mechanism including a sun gear Sc, a ring gear Rc, and a carrier Cc that axially supports a pinion Pc engaging with the sun gear Sc and the ring gear Rc in a rotatable and revolvable manner.
  • the so-called single pinion type planetary gear mechanism is also referred to as a minus planetary gear mechanism or a negative planetary gear mechanism, because, when the carrier is fixed and the sun gear is rotated, the ring gear rotates in a direction different from the rotating direction of the sun gear.
  • the so-called single pinion type planetary gear mechanism when the ring gear is fixed and the sun gear is rotated, the carrier rotates in the same direction as the sun gear.
  • the third planetary gear mechanism PG 3 illustrated in the second stage from the top of FIG. 3
  • three elements Sc, Cc, and Rc of the third planetary gear mechanism PG 3 are a first element, a second element, and a third element from the left in an arrangement order at intervals corresponding to a gear ratio (the number of teeth of the ring gear/the number of teeth of the sun gear) in the nomogram
  • the first element is the sun gear Sc
  • the second element is the carrier Cc
  • the third element is the ring gear Re.
  • a ratio of the interval between the sun gear Sc and the carrier Cc and the interval between the carrier Cc and the ring gear Rc is set to h:1, where h denotes a gear ratio of the third planetary gear mechanism PG 3 .
  • h denotes a gear ratio of the third planetary gear mechanism PG 3 .
  • a lower horizontal line and an upper horizontal line denote that the rotation speeds thereof are “0” and “1” (the same rotation speed as the input shaft 11 ), respectively.
  • the fourth planetary gear mechanism PG 4 is configured as a so-called single pinion type planetary gear mechanism including a sun gear Sd, a ring gear Rd, and a carrier Cd that axially supports a pinion Pd engaging with the sun gear Sd and the ring gear Rd in a rotatable and revolvable manner.
  • the fourth element is the ring gear Rd
  • the fifth element is the carrier Cd
  • the sixth element is the sun gear Sd.
  • a ratio of the interval between the sun gear Sd and the carrier Cd and the interval between the carrier Cd and the ring gear Rd is set to i:1, where i denotes the gear ratio of the fourth planetary gear mechanism PG 4 .
  • the first planetary gear mechanism PG 1 is configured as a so-called single pinion type planetary gear mechanism including a sun gear Sa, a ring gear Ra, and a carrier Ca that axially supports a pinion Pa engaging with the sun gear Sa and the ring gear Ra in a rotatable and revolvable manner.
  • the seventh element is the sun gear Sa
  • the eighth element is the carrier Ca
  • the ninth element is the ring gear Ra.
  • a ratio of the interval between the sun gear Sa and the carrier Ca and the interval between the carrier Ca and the ring gear Ra is set to j:1, where j denotes the gear ratio of the first planetary gear mechanism PG 1 .
  • the second planetary gear mechanism PG 2 is configured as a so-called single pinion type planetary gear mechanism including a sun gear Sb, a ring gear Rb, and a carrier Cb that axially supports a pinion Pb engaging with the sun gear Sb and the ring gear Rb in a rotatable and revolvable manner.
  • the tenth element is the ring gear Rb
  • the eleventh element is the carrier Cb
  • the twelfth element is the sun gear Sb.
  • a ratio of the interval between the sun gear Sb and the carrier Cb and the interval between the carrier Cb and the ring gear Rb is set to k:1, where k denotes the gear ratio of the second planetary gear mechanism PG 2 .
  • the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 is connected to the input shaft 11 (a second input shaft 11 b which will be described later).
  • the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 is connected to the output member 13 including an output gear.
  • the carrier Cc (the second element) of the third planetary gear mechanism PG 3 , the carrier Cd (the fifth element) of the fourth planetary gear mechanism PG 4 , and the ring gear Ra (the ninth element) of the first planetary gear mechanism PG 1 are connected to form a first connected structure Cc-Cd-Ra.
  • the ring gear Rc (the third element) of the third planetary gear mechanism PG 3 and the sun gear Sb (the twelfth element) of the second planetary gear mechanism PG 2 are connected to form a second connected structure Rc-Sb.
  • the carrier Ca (the eighth element) of the first planetary gear mechanism PG 1 and the carrier Cb (the eleventh element) of the second planetary gear mechanism PG 2 are connected to form a third connected structure Ca-Cb.
  • the automatic transmission according to this embodiment includes seven engagement mechanisms including three clutches, that is, first to third clutches C 1 to C 3 , three brakes, that is, first to third brakes B 1 to B 3 , and one two-way clutch F 1 .
  • the first clutch C 1 is a hydraulically actuated type wet multi-disc clutch and is configured to be switchable between a connected state in which the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 is connected to the third connected structure Ca-Cb and a disconnected state (open state) in which the connection is cut.
  • An input side of the first clutch C 1 is connected to the input shaft 11 (a first input shaft 11 a which will be described later).
  • the third clutch C 3 is a hydraulically actuated type wet multi-disc clutch and is configured to be switchable between a connected state in which the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 is connected to the ring gear Rd (the fourth element) of the fourth planetary gear mechanism PG 4 and a disconnected state in which the connection is cut.
  • the second clutch C 2 is a hydraulically actuated type wet multi-disc clutch and is configured to be switchable between a connected state in which the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 is connected to the second connected structure Rc-Sb and a disconnected state in which the connection is cut.
  • the two-way clutch F 1 also has a function of a fourth brake and is configured to be switchable between a reverse rotation prohibited state in which forward rotation (rotation in the same direction as the rotating direction of the input shaft 11 and the output member 13 ) of the third connected structure Ca-Cb is permitted and reverse rotation thereof is prohibited and a fixed state in which the third connected structure Ca-Cb is fixed to the transmission case 10 .
  • the two-way clutch F 1 In the reverse rotation prohibited state, when a force for rotating in the forward rotating direction is applied to the third connected structure Ca-Cb, the rotation is permitted and the two-way clutch F 1 is switched to the disconnected state. When a force for rotating in the reverse rotating direction is applied thereto, the rotation is prohibited and the two-way clutch F 1 is switched to the fixed state in which the third connected structure is fixed to the transmission case 10 .
  • the two-way clutch F 1 corresponds to a switching mechanism.
  • the first brake B 1 is a hydraulically actuated type wet multi-disc brake and is configured to be switchable between a fixed state in which the sun gear Sa (the seventh element) of the first planetary gear mechanism PG 1 is fixed to the transmission case 10 and a disconnected state in which the fixation is released.
  • the second brake B 2 is a hydraulically actuated type wet multi-disc brake and is configured to be switchable between a fixed state in which the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 is fixed to the transmission case 10 and a disconnected state in which the fixation is released.
  • the third brake B 3 is a hydraulically actuated type wet multi-disc brake and is configured to be switchable between a fixed state in which the ring gear Rd (the fourth element) of the fourth planetary gear mechanism PG 4 is fixed to the transmission case 10 and a disconnected state in which the fixation is released.
  • the states of the clutches C 1 to C 3 , the brakes B 1 to B 3 , and the two-way clutch F 1 are switched on the basis of vehicle information such as a traveling speed of the vehicle by the gear shift controller ECU including a transmission control unit (TCU) illustrated in FIG. 1 .
  • vehicle information such as a traveling speed of the vehicle by the gear shift controller ECU including a transmission control unit (TCU) illustrated in FIG. 1 .
  • TCU transmission control unit
  • the gear shift controller ECU is configured as an electronic control unit including a CPU and a memory which are not illustrated, can receive predetermined vehicle information such as a traveling speed or an accelerator opening degree of the vehicle V, a rotation speed or an output torque of the engine E, or operation information of a paddle shift lever 33 , and controls the automatic transmission 3 (a gear shift mechanism) by causing the CPU to execute a control program stored in a storage device such as the memory.
  • vehicle information such as a traveling speed or an accelerator opening degree of the vehicle V, a rotation speed or an output torque of the engine E, or operation information of a paddle shift lever 33 .
  • the paddle shift lever 33 is provided in a steering wheel 31 of the vehicle V according to this embodiment, the gear stage is upshifted manually by pulling a right paddle 33 u forward, and the gear stage is downshifted manually by pulling a left paddle 33 d forward.
  • An operation signal of the paddle shift lever 33 is transmitted to the gear shift controller ECU.
  • An operation unit for manual operation in the disclosure is not limited to the paddle shift lever 33 according to the embodiment, but another operation unit such as a shift lever disposed between a driver seat and a passenger seat or a button disposed in a steering wheel may be used.
  • the first clutch C 1 , the first planetary gear mechanism PG 1 , the second planetary gear mechanism PG 2 , the third planetary gear mechanism PG 3 , the second clutch C 2 , the fourth planetary gear mechanism PG 4 , and the third clutch C 3 are sequentially arranged from the engine E and the torque converter 2 side.
  • the third brake B 3 is disposed outside in the radial direction of the fourth planetary gear mechanism PG 4
  • the second brake B 2 is disposed outside in the radial direction of the second clutch C 2
  • the first brake B 1 is disposed outside in the radial direction of the first clutch C 1
  • the two-way clutch F 1 is disposed outside in the radial direction of the first planetary gear mechanism PG 1 .
  • the three brakes B 1 to B 3 and the two-way clutch F 1 are arranged outside in the radial direction of the planetary gear mechanisms or the clutches, it is possible to achieve a decrease in axial length of the automatic transmission 3 in comparison with a case in which the brakes B 1 to B 3 and the two-way clutch F 1 along with the planetary gear mechanisms and the clutches are arranged on the axis of the input shaft 11 .
  • the third brake B 3 may be disposed outside in the radial direction of the third clutch C 3 and the second brake B 2 may be disposed outside in the radial direction of the fourth planetary gear mechanism PG 4 .
  • the two-way clutch F 1 When a first gear stage is set up, the two-way clutch F 1 is set to the reverse rotation prohibited state (R in FIG. 4 ) and the first brake B 1 and the second brake B 2 are set to the fixed state.
  • the two-way clutch F 1 By setting the two-way clutch F 1 to the reverse rotation prohibited state (R) and setting the first brake B 1 to the fixed state, reverse rotation of the third connected structure Ca-Cb and the sun gear Sa (the seventh element) of the first planetary gear mechanism PG 1 is prohibited and the rotation speed of the third connected structure Ca-Cb and the sun gear Sa (the seventh element) of the first planetary gear mechanism PG 1 is “0.”
  • three elements of the seventh to ninth elements Sa, Ca, and Ra of the first planetary gear mechanism PG 1 are in a locked state in which relative rotation is not possible, and the rotation speed of the first connected structure Cc-Cd-Ra including the ring gear Ra (the ninth element) of the first planetary gear mechanism PG 1 is “0.”
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “1st” which is illustrated in FIG. 3 and the first gear stage is set up.
  • the second brake B 2 is set to the fixed state at the first gear stage such that smooth shift from the first gear stage to a second gear stage which will be described later is achieved.
  • the two-way clutch F 1 can be switched from the reverse rotation prohibited state (R) to the fixed state (L).
  • the two-way clutch F 1 is set to the reverse rotation prohibited state (R)
  • the first brake B 1 and the second brake B 2 are set to the fixed state
  • the second clutch C 2 is set to the connected state.
  • forward rotation of the third connected structure Ca-Cb is permitted.
  • the rotation speed of the sun gear Sa (the seventh element) of the first planetary gear mechanism PG 1 is “0.”
  • the rotation speed of the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 is “0.”
  • the rotation speed of the second connected structure Rc-Sb is “0” which is the same as the rotation speed of the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 .
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “2nd” which is illustrated in FIG. 3 and the second gear stage is set up.
  • the two-way clutch F 1 When a third gear stage is set up, the two-way clutch F 1 is set to the reverse rotation prohibited state, the first brake B 1 and the second brake B 2 are set to the fixed state, and the third clutch C 3 is set to the connected state.
  • the two-way clutch F 1 By setting the two-way clutch F 1 to the reverse rotation prohibited state, forward rotation of the third connected structure Ca-Cb is permitted.
  • the rotation speed of the sun gear Sa (the seventh element) of the first planetary gear mechanism PG 1 By setting the second brake B 2 to the fixed state, the rotation speed of the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 is “0.”
  • the rotation speed of the ring gear Rd (the fourth element) of the fourth planetary gear mechanism PG 4 is “1” which is the same as the rotation speed of the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 which is connected to the input shaft 11 . Since the rotation speed of the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 is “0” and the rotation speed of the ring gear Rd (the fourth element) is “1,” the rotation speed of the carrier Cd (the fifth element), that is, the rotation speed of the first connected structure Cc-Cd-Ra, is i/(i+1).
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “3rd” which is illustrated in FIG. 3 and the third gear stage is set up.
  • the two-way clutch F 1 When a fourth gear stage is set up, the two-way clutch F 1 is set to the reverse rotation prohibited state, the first brake B 1 is set to the fixed state, and the second clutch C 2 and the third clutch C 3 are set to the connected state.
  • the two-way clutch F 1 By setting the two-way clutch F 1 to the reverse rotation prohibited state, forward rotation of the third connected structure Ca-Cb is permitted.
  • the rotation speed of the sun gear Sa (the seventh element) of the first planetary gear mechanism PG 1 is “0.”
  • the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 and the second connected structure Rc-Sb rotate at the same speed. Accordingly, in the third planetary gear mechanism PG 3 and the fourth planetary gear mechanism PG 4 , the carrier Cc (the second element) and the carrier Cd (the fifth element) are connected, and the ring gear Rc (the third element) and the sun gear Sd (the sixth element) are connected.
  • the fourth gear stage at which the second clutch C 2 is set to the connected state one nomogram including four elements can be drawn with the third planetary gear mechanism PG 3 and the fourth planetary gear mechanism PG 4 .
  • the rotation speed of the ring gear Rd (the fourth element) of the fourth planetary gear mechanism PG 4 is “1” which is the same as the rotation speed of the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 , and the rotation speeds of two elements among four elements in the third planetary gear mechanism PG 3 and the fourth planetary gear mechanism PG 4 are “1” which is the same speed.
  • the elements of the third planetary gear mechanism PG 3 and the fourth planetary gear mechanism PG 4 are in the locked state in which relative rotation is not possible, and the rotation speed of all the elements of the third planetary gear mechanism PG 3 and the fourth planetary gear mechanism PG 4 is “1.”
  • the rotation speed of the third connected structure Ca-Cb is j/(j+1)
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “4th” which is illustrated in FIG. 3 and the fourth gear stage is set up.
  • the two-way clutch F 1 When a fifth gear stage is set up, the two-way clutch F 1 is set to the reverse rotation prohibited state, the first brake B 1 is set to the fixed state, and the first clutch C 1 and the third clutch C 3 are set to the connected state.
  • the two-way clutch F 1 By setting the two-way clutch F 1 to the reverse rotation prohibited state, forward rotation of the third connected structure Ca-Cb is permitted.
  • the rotation speed of the sun gear Sa (the seventh element) of the first planetary gear mechanism PG 1 is “0.”
  • the rotation speed of the third connected structure Ca-Cb is “1” which is the same as the rotation speed of the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 .
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “5th” which is illustrated in FIG. 3 and the fifth gear stage is set up.
  • the third clutch C 3 In order to set up the fifth gear stage, it is not necessary to set the third clutch C 3 to the connected state. However, since the third clutch needs to be set to the connected state at the fourth gear stage and a sixth gear stage which will be described later, the third clutch C 3 is set to the connected state at the fifth gear stage such that smooth downshift from the fifth gear stage to the fourth gear stage and upshift from the fifth gear stage to the sixth gear stage which will be described later are achieved.
  • the two-way clutch F 1 is set to the reverse rotation prohibited state, and three clutches of the first to third clutches C 1 to C 3 are set to the connected state.
  • the two-way clutch F 1 By setting the two-way clutch F 1 to the reverse rotation prohibited state, forward rotation of the third connected structure Ca-Cb is permitted.
  • the carrier Cb (the eleventh element) and the sun gear Sb (the twelfth element) of the second planetary gear mechanism PG 2 have the same rotation speed “1,” and the elements are in the locked state in which relative rotation is not possible.
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “1” of the “6th” which is illustrated in FIG. 3 and the sixth, gear stage is set up.
  • the two-way clutch F 1 When a seventh gear stage is set up, the two-way clutch F 1 is set to the reverse rotation prohibited state, the second brake B 2 is set to the fixed state, and the first clutch C 1 and the third clutch C 3 are set to the connected state.
  • the two-way clutch F 1 By setting the two-way clutch F 1 to the reverse rotation prohibited state, forward rotation of the third connected structure Ca-Cb is permitted.
  • the rotation speed of the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 is “0.”
  • the rotation speed of the ring gear Rd (the fourth element) of the fourth planetary gear mechanism PG 4 is “1” which is the same as the rotation speed of the sun gear Sc (the first element) of the third planetary gear mechanism PG 3
  • the rotation speeds of the first connected structure Cc-Cd-Ra including the carrier Cd (the fifth element) of the fourth planetary gear mechanism PG 4 is i/(i+1).
  • the rotation speed of the third connected structure Ca-Cb is “1” which is the same as the rotation speed of the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 connected to the input shaft 11 .
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “7th” which is illustrated in FIG. 3 and the seventh gear stage is set up.
  • the two-way clutch F 1 is set to the reverse rotation prohibited state
  • the second brake B 2 is set to the fixed state
  • the first clutch C 1 and the second clutch C 2 are set to the connected state.
  • the rotation speed of the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 is “0.”
  • the rotation speed of the second connected structure Rc-Sb is “0” which is the same as the rotation speed of the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 .
  • the rotation speed of the third connected structure Ca-Cb is “1” which is the same as the rotation speed of the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 .
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “8th” which is illustrated in FIG. 3 and the eighth gear stage is set up.
  • the two-way clutch F 1 is set to the reverse rotation prohibited state
  • the second brake B 2 and the third brake B 3 are set to the fixed state
  • the first clutch C 1 is set to the connected state.
  • the rotation speed of the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 is “0.”
  • the ring gear Rd (the fourth element) of the fourth planetary gear mechanism PG 4 is also “0.” Accordingly, the elements Sd, Cd, and Rd of the fourth planetary gear mechanism PG 4 are in the locked state in which relative rotation is not possible, and the rotation speed of the first connected structure Cc-Cd-Ra including the carrier Cd (the fifth element) of the fourth planetary gear mechanism PG 4 is also “0.”
  • the rotation speed of the third connected structure Ca-Cb is “1” which is the same as the rotation speed of the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 .
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “9th” which is illustrated in FIG. 3 and the ninth gear stage is set up.
  • the two-way clutch F 1 When a tenth gear stage is set up, the two-way clutch F 1 is set to the reverse rotation prohibited state, the third brake B 23 is set to the fixed state, and the first clutch C 1 and the second clutch C 2 are set to the connected state. By setting the two-way clutch F 1 to the reverse rotation prohibited state, forward rotation of the third connected structure Ca-Cb is permitted.
  • the second clutch C 2 By setting the second clutch C 2 to the connected state, the second connected structure Rc-Sb and the sun gear Sd (the sixth element) of the fourth planetary gear mechanism PG 4 rotate at the same speed.
  • the rotation speed of the ring gear Rd (the fourth element) of the fourth planetary gear mechanism PG 4 is “0.”
  • the rotation speed of the third connected structure Ca-Cb is “1” which is the same as the rotation speed of the sun gear Sc (the first element) of the third planetary gear mechanism PG 3 .
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “10th” which is illustrated in FIG. 3 and the tenth gear stage is set up.
  • the two-way clutch F 1 is set to the fixed state (L in FIG. 4 ), the second brake B 2 is set to the fixed state, and the third clutch C 3 is set to the connected state.
  • the rotation speed of the first connected structure Cc-Cd-Ra is i/(i+1).
  • the rotation speed of the third connected structure Ca-Cb is “0.”
  • the rotation speed of the ring gear Rb (the tenth element) of the second planetary gear mechanism PG 2 which is connected to the output member 13 is “Rvs” indicating reverse rotation which is illustrated in FIG. 3 and the reverse gear stage is set up.
  • Speed lines indicated by dotted lines in FIG. 3 represent that the elements of the other planetary gear mechanism rotate (idle) to follow the planetary gear mechanism that transmits power among the four planetary gear mechanisms PG 1 to PG 4 .
  • FIG. 4 is a diagram collectively illustrating the states of the clutches C 1 to C 3 , the brakes B 1 to B 3 , and the two-way clutch F 1 at the above-mentioned gear stages.
  • “0” in columns of three clutches of the first to third clutches C 1 to C 3 and three brakes of the first to third brakes B 1 to B 3 represents the connected state or the fixed state, and blanks represent the disconnected state.
  • “R” in the column of the two-way clutch F 1 represents the reverse rotation prohibited state, and “L” indicates the fixed state.
  • gear shift ratios of the gear stages (the rotation speed of the input shaft 11 /the rotation speed of the output member 13 ) and a common ratio (a ratio of the gear shift ratios between the gear stages, which is a value obtained by dividing the gear shift ratio of a predetermined gear stage by the gear shift ratio of the gear stage immediately higher than the predetermined gear stage) are illustrated where the gear ratio h of the third planetary gear mechanism PG 3 is 2.734, the gear ratio i of the fourth planetary gear mechanism PG 4 is 1.614, the gear ratio j of the first planetary gear mechanism PG 1 is 2.681, and the gear ratio k of the second planetary gear mechanism PG 2 is 1.914. It can be seen therefrom that the common ratio can be appropriately set.
  • the two-way clutch F 1 will be described below in detail with reference to FIGS. 5 to 8 .
  • the two-way clutch F 1 is configured to be switchable between the fixed state in which the third connected structure Ca-Cb is fixed to the transmission case 10 and the reverse rotation prohibited state in which forward rotation of the third connected structure Ca-Cb is permitted and reverse rotation thereof is prohibited.
  • the two-way clutch F 1 includes a fixed plate TW 11 which is fixed to the transmission case 10 and a rotary plate TW 12 .
  • the fixed plate TW 11 is formed in an annular shape (a doughnut shape).
  • the rotary plate TW 12 is also formed in an annular shape (a doughnut shape) similarly to the fixed plate TW 11 .
  • the fixed plate TW 11 and the rotary plate TW 12 are arranged concentric with each other.
  • Storage portions TW 15 and TW 16 recessed to store the swing portion on a forward rotation prohibition side TW 13 and the swing portion on a reverse rotation prohibition side TW 14 are provided on the opposed surface TW 11 a of the fixed plate TW 11 .
  • Bias members TW 17 a and TW 17 b including springs that bias the swing portions TW 13 and TW 14 such that the swinging ends TW 13 a and TW 14 a of the corresponding swing portions TW 13 and TW 14 protrude from the storage portions TW 15 and TW 16 are provided on the bottom surfaces of the storage portions TW 15 and TW 16 .
  • Pit portions TW 18 and TW 19 are provided at positions corresponding to the swing portions TW 13 and TW 14 on an opposed surface TW 12 a of the rotary plate TW 12 opposing the fixed plate TW 11 .
  • a first engagement portion TW 18 a that is located on the other side in the circumferential direction (the reverse rotating direction) of the rotary plate TW 12 and that is formed in a step shape capable of engaging with the swinging end TW 13 a of the swing portion on a forward rotation prohibition side TW 13 is provided in the first pit portion TW 18 which is formed at the position corresponding to the swing portion on a forward rotation prohibition side TW 13 .
  • a second engagement portion TW 19 a that is located on one side in the circumferential direction (the forward rotating direction) of the rotary plate TW 12 and that is formed in a step shape capable of engaging with the swinging end TW 14 a of the swing portion on a reverse rotation prohibition side TW 14 is provided in the second pit portion TW 19 which is formed at the position corresponding to the swing portion on a reverse rotation prohibition side TW 14 .
  • a switching plate TW 20 is interposed between the fixed plate TW 11 and the rotary plate TW 12 . As illustrated in FIG. 7 , the switching plate TW 20 is also formed in an annular shape (a doughnut shape). In the switching plate TW 20 , cutout holes TW 20 a and TW 20 b are formed at positions corresponding to the swing portions TW 13 and TW 14 .
  • a protrusion TW 20 c that protrudes outward in the radial direction is provided in an outer edge of the switching plate TW 20 .
  • the switching plate TW 20 is configured to swing about the fixed plate TW 11 .
  • the second cutout hole TW 20 b corresponding to the swing portion on a reverse rotation prohibition side TW 14 is configured such that the swing portion on a reverse rotation prohibition side TW 14 is not stored in the storage portion TW 16 and the end TW 14 a engages with the second engagement portion TW 19 a as illustrated in FIG. 8 .
  • the state illustrated in FIGS. 6 and 8 is the reverse rotation prohibited state of the two-way clutch F 1 .
  • a lubricant supply structure in an idling shaft 23 (a rotary shaft) according to the gist of the disclosure will be described below with reference to FIGS. 9 and 10 .
  • both ends of the idling shaft 23 are rotatably supported by the transmission case 10 via bearings (a first bearing BRG 1 and a second bearing BRG 2 ) which are a pair of bearings.
  • a lubricant passage 231 that extends in an axial direction and discharge holes 232 that communicate with the lubricant passage 231 and that are opened at an attachment position of an idling gear 21 (a part which is spline-fitted) are formed in the idling shaft 23 .
  • a circular discharge space 233 as a discharge channel is formed between an end of the lubricant passage 231 open on a side of the idling shaft 23 supported by the first bearing BRG 1 and an inner surface of the transmission case 10 .
  • Supply of a lubricant to the first bearing BRG 1 is performed via the discharge space 233 .
  • the oil pipe 40 is inserted into the lubricant passage 231 of the idling shaft 23 .
  • the oil pipe 40 includes an annular convex portion 41 that extends from an outer surface on the side of one end (a right end in the drawing) in a flange shape, a large-diameter portion 42 that has a diameter larger than that of the other part on the side of the other end (a left end in the drawing), and a tapered portion 43 that decreases gradually in diameter toward the other end (the left end in the drawing) from the large-diameter portion 42 .
  • the large-diameter portion 42 increases gradually in diameter via an inclined portion 44 from the other end of the oil pipe 40 .
  • a pair of first communication holes 45 and a pair of second communication holes 46 are formed in the oil pipe 40 .
  • the tapered portion 43 and the large-diameter portion 42 of the oil pipe 40 are inserted into an insertion hole 401 formed on the inner surface of the transmission case 10 , and an end opposite to the tapered portion 43 is inserted into an oil introducing portion 402 formed in the transmission case 10 .
  • the oil introducing portion 402 is connected to a lubricant source which is not illustrated in the drawing and a lubricant is introduced into the oil pipe 40 from the oil introducing portion 402 .
  • the first communication holes 45 and the second communication holes 46 formed in the oil pipe 40 communicate with the lubricant passage 231 at a position between the discharge hole 232 and the discharge space 233 .
  • This position is a position corresponding to the lubricant passage 231 on the insertion hole 401 side.
  • a lubricant introduced into the oil pipe 40 flows in the oil pipe 40 , reaches the first communication holes 45 and the second communication holes 46 , and flows out of the first communication holes 45 and the second communication holes 46 to the lubricant passage 231 at a position between the discharge hole 232 and the discharge space 233 .
  • the lubricant which is affected by a centrifugal force with the rotation of the idling shaft 23 flows along the inner surface of the lubricant passage 231 and flows to the discharge hole 232 and the discharge space 233 .
  • a stepped portion 231 a is formed in the lubricant passage 231 by decreasing the inner diameter of the lubricant passage 231 .
  • the lubricant is dammed by the stepped portion 231 a , a flow of the lubricant toward the oil introducing portion 402 is restricted, and thus supply of the lubricant to an unnecessary part is prohibited.
  • a first annular protruding portion 233 a that protrudes to a space between the idling shaft 23 and the first bearing BRG 1 is formed on the inner surface of the transmission case 10 which forms the discharge space 233 .
  • a second annular protruding portion 233 b that protrudes along the outer circumference of the insertion hole 401 for the oil pipe 40 is formed on the inner surface of the transmission case 10 .
  • An inclined guide surface 231 b that expands gradually from the inside to the outside of the lubricant passage 231 is formed at an edge of the lubricant passage 231 which is continuous from the discharge space 231 .
  • the first bearing BRG 1 supports the idling shaft 23 at the outer circumference of an end thereof. Accordingly, the first bearing BRG 1 is located inside in the axial direction from the end of the idling shaft 23 , and a tip of a retainer BRG 1 a which is a component of the first bearing BRG 1 protrudes slightly outside in the axial direction from the end of the idling shaft 23 . Accordingly, there is concern that the supply of a lubricant to the first bearing BRG 1 will not be sufficient by only discharging the lubricant two-dimensionally in the radial direction from the edge of the lubricant passage 231 .
  • the first annular protruding portion 233 a is provided on the inner surface of the transmission case 10 . Accordingly, an inside inclined surface of the first annular protruding portion 233 a can guide the lubricant to the tip of the retainer BRG 1 a of the first bearing BRG 1 .
  • the lubricant flowing along the inner surface of the lubricant passage 231 and going straightly to the inner surface of the transmission case 10 is smoothly changed in direction to the radial direction by an outside inclined surface of the second annular protruding portion 233 b . Accordingly, the lubricant flowing along the inner surface of the lubricant passage 231 can be smoothly bent to the radial direction and can be caused to flow to the discharge space 233 .
  • the lubricant flows smoothly to the discharge space 233 along the inclined guide surface 231 b due to the centrifugal force of the rotating idling shaft 23 .
  • the lubricant intruding from the outside is guided to the first bearing BRG 1 by the outside inclined surface of the first annular protruding portion 233 a on the inner surface of the transmission case 10 . Accordingly, the lubricant intruding from the outside can be usefully used for lubrication of the first bearing BRG 1 , and the lubrication intruding from the outside can also be prevented from intruding into the lubricant passage 231 .
  • a so-called taper roller bearing is employed as the first bearing BRG 1 (a bearing), but the disclosure is not limited thereto.
  • a so-called ball bearing may be employed.
  • one gear stage (for example, the tenth gear stage) may be omitted to perform forward gear shift of nine gear stages.
  • switching of a shift position is performed by manually operating the paddle shift lever 33 .
  • the method of switching the shift position is not limited thereto, but the shift position may be switched, for example, by pushing a button.
  • a selected shift position may be determined on the basis of a push signal of the button.
  • the two-way clutch F 1 is used, but a wet multi-disc brake and a one-way clutch installed in the brake may be provided instead of the two-way clutch F 1 .
  • the one-way clutch can be configured to permit forward rotation of the third connected structure Ca-Cb and to prohibit reverse rotation thereof, and the wet multi-disc brake can be engaged only when it is wanted to use an engine brake at the reverse gear stage and the first gear stage.
  • the gear shift mechanism (the automatic transmission 3 ) that can set up each gear stage by engaging three engagement mechanisms is used, but the disclosure can also be applied to a gear shift mechanism that can set up each gear stage by engaging two engagement mechanisms or a gear shift mechanism that can set up each gear stage by engaging four or more engagement mechanisms. In this case, the same advantages can be obtained.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • General Details Of Gearings (AREA)
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FR3048746B1 (fr) * 2016-03-10 2019-04-26 Renault S.A.S Dispositif de lubrification d'un arbre creux et boite de vitesses comportant une canule d'alimentation fixe
US11519490B2 (en) 2019-02-13 2022-12-06 Honda Motor Co., Ltd. Oil supply unit

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5142861A (ja) 1974-10-09 1976-04-12 Aisin Seiki Juseihagurumasochino junkatsusochi
JPS58157060A (ja) 1982-03-13 1983-09-19 Hitachi Maxell Ltd 渦巻形電池の製造方法
JPS616065A (ja) 1984-06-18 1986-01-11 財団法人鉄道総合技術研究所 鉄道車両用台車
JP2000240772A (ja) 1999-02-22 2000-09-05 Honda Motor Co Ltd 変速機の潤滑油供給構造
JP2003049910A (ja) 2001-08-02 2003-02-21 Daihatsu Motor Co Ltd 無段変速機
JP2005054874A (ja) 2003-08-04 2005-03-03 Kubota Corp エンジンの出力歯車列におけるアイドルギヤの軸受装置
US20060054409A1 (en) * 2004-09-15 2006-03-16 Takeshi Miyazaki Oil supplying structure of transmission for vehicle
US20070111839A1 (en) * 2005-11-11 2007-05-17 Young Sam Choi Planetary gear set for an automatic transmission of a vehicle
CN102168749A (zh) 2010-02-25 2011-08-31 丰田自动车株式会社 车辆动力传递装置
CN103225694A (zh) 2012-01-31 2013-07-31 住友重机械工业株式会社 输送装置
US20140213405A1 (en) * 2011-09-29 2014-07-31 Aisin Aw Co., Ltd. Power transmission device
KR101519380B1 (ko) 2013-09-24 2015-05-13 현대 파워텍 주식회사 자동변속기용 윤활제 공급장치
US20150252945A1 (en) * 2014-03-10 2015-09-10 Toyota Motor Engineering & Manufacturing North America, Inc. Flow-restricting plug and differential drive pinion having the same
US20150337945A1 (en) * 2014-05-20 2015-11-26 Deere & Company Shaft retention and lubrication system and method

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58157060U (ja) * 1982-04-16 1983-10-20 愛知機械工業株式会社 歯車変速機の潤滑装置
JPS616065U (ja) * 1984-06-18 1986-01-14 トヨタ自動車株式会社 回転体部材の潤滑装置
JP2010101399A (ja) * 2008-10-23 2010-05-06 Ud Trucks Corp 変速機の潤滑構造

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5142861A (ja) 1974-10-09 1976-04-12 Aisin Seiki Juseihagurumasochino junkatsusochi
JPS58157060A (ja) 1982-03-13 1983-09-19 Hitachi Maxell Ltd 渦巻形電池の製造方法
JPS616065A (ja) 1984-06-18 1986-01-11 財団法人鉄道総合技術研究所 鉄道車両用台車
JP2000240772A (ja) 1999-02-22 2000-09-05 Honda Motor Co Ltd 変速機の潤滑油供給構造
JP2003049910A (ja) 2001-08-02 2003-02-21 Daihatsu Motor Co Ltd 無段変速機
JP2005054874A (ja) 2003-08-04 2005-03-03 Kubota Corp エンジンの出力歯車列におけるアイドルギヤの軸受装置
US20060054409A1 (en) * 2004-09-15 2006-03-16 Takeshi Miyazaki Oil supplying structure of transmission for vehicle
US20070111839A1 (en) * 2005-11-11 2007-05-17 Young Sam Choi Planetary gear set for an automatic transmission of a vehicle
CN102168749A (zh) 2010-02-25 2011-08-31 丰田自动车株式会社 车辆动力传递装置
US20140213405A1 (en) * 2011-09-29 2014-07-31 Aisin Aw Co., Ltd. Power transmission device
CN103225694A (zh) 2012-01-31 2013-07-31 住友重机械工业株式会社 输送装置
KR101519380B1 (ko) 2013-09-24 2015-05-13 현대 파워텍 주식회사 자동변속기용 윤활제 공급장치
US20150252945A1 (en) * 2014-03-10 2015-09-10 Toyota Motor Engineering & Manufacturing North America, Inc. Flow-restricting plug and differential drive pinion having the same
US20150337945A1 (en) * 2014-05-20 2015-11-26 Deere & Company Shaft retention and lubrication system and method

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
"Office Action of China Counterpart Application", dated Jul. 27, 2020, with English translation thereof, pp. 1-11.
"Office Action of China Counterpart Application," with machine English translation thereof, dated Jan. 6, 2020, p. 1-p. 10.
"Office Action of Japan Counterpart Application," with English translation thereof, dated Jul. 24, 2018, p. 1-p. 5.

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JP2018159394A (ja) 2018-10-11

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